EP1704929A1 - Oscillating drive especially eccentric drive for vibrating machines - Google Patents

Oscillating drive especially eccentric drive for vibrating machines Download PDF

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Publication number
EP1704929A1
EP1704929A1 EP06004701A EP06004701A EP1704929A1 EP 1704929 A1 EP1704929 A1 EP 1704929A1 EP 06004701 A EP06004701 A EP 06004701A EP 06004701 A EP06004701 A EP 06004701A EP 1704929 A1 EP1704929 A1 EP 1704929A1
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EP
European Patent Office
Prior art keywords
eccentric
drive
sleeve
eccentric shaft
cylinder housing
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Granted
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EP06004701A
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German (de)
French (fr)
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EP1704929B1 (en
Inventor
Klaus Lambart
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Schenck Process Europe GmbH
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Schenck Process GmbH
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G27/00—Jigging conveyors
    • B65G27/10—Applications of devices for generating or transmitting jigging movements
    • B65G27/32—Applications of devices for generating or transmitting jigging movements with means for controlling direction, frequency or amplitude of vibration or shaking movement
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • B06B1/162—Making use of masses with adjustable amount of eccentricity
    • B06B1/163—Making use of masses with adjustable amount of eccentricity the amount of eccentricity being only adjustable when the system is stationary

Definitions

  • Vibratory conveyors are continuous conveyors used to convey or treat bulk and general cargo.
  • One application of vibrating machines is, for example, in foundries, whereby castings can be transported over longer transport routes and treated at the same time.
  • Another area of use is, for example, the ash discharge in waste incineration plants.
  • the vibrating machines have a conveyor bottom, which can be formed in tube or channel shape.
  • a so-called vibration drive puts the conveyor floor in a periodic oscillating motion, whereby a conveying movement of the goods located on the conveyor floor can be achieved.
  • different vibration drives are used in practice.
  • Such a vibration drive is the so-called push crank or eccentric drive.
  • This consists essentially of a rotatably mounted in a housing eccentric shaft, wherein the housing is connected via a push rod with the conveyor bottom.
  • the oscillatory movement of the conveyor floor is essentially determined by the number of oscillations, the amplitude and the swing angle, with practical interest, the conveying speed and thus the flow rate.
  • the conveying speed of the material to be conveyed is Use of a sliding-crank drive, among other things depending on the fixed eccentric radius of the eccentric shaft used. In this case, a drive can be used only for certain goods to be conveyed and delivery speeds at the fixed eccentric radius. If the operating conditions change, the entire thrust crank drive must be replaced and / or rebuilt. This requires complex assembly or retooling, which are associated with high costs and long assembly times and downtime of the vibratory conveyor and the associated system parts.
  • the object of the present invention is therefore to develop an eccentric drive for vibrating machines in such a way that, under changed conditions of use, a quick and simple change of the vibration data, in particular the conveying speed of the vibration conveyor, is possible.
  • the vibration drive according to the invention comprises an eccentric shaft (eccentric shaft) which is mounted in an eccentric sleeve (eccentric sleeve) and the position between the eccentric shaft and the eccentric sleeve can be set arbitrarily.
  • the eccentric radius can be changed in a very wide range in millimeter increments. With changed operating conditions, a required eccentricity can thus be set without expensive retooling.
  • the set position is then fixed by non-positive and / or positive locking means.
  • hydromechanical fixing means wherein a hydraulic sleeve member for clamping and releasing the position of the eccentric shaft and the eccentric sleeve is arranged.
  • a hydraulic sleeve member for clamping and releasing the position of the eccentric shaft and the eccentric sleeve is arranged.
  • the fixing means is designed such that a non-positive fixing of the position of the eccentric shaft to the eccentric sleeve is effected by means of mechanical clamping.
  • the eccentric sleeve is designed slotted, the clamp is adjustable by a screw.
  • a vibrating machine 1 is shown with the vibration drive 2 according to the invention in a schematic representation.
  • the vibrating machine 1 is designed as a vibrating conveyor for conveying piece goods, for example, castings. However, any other fields of use are possible.
  • the vibratory conveyor 1 can also be designed as a vibrating screen.
  • the vibratory conveyor 1 has a conveyor bottom 3, which is arranged in a swing frame 4.
  • the swing frame 4 is coupled for the purpose of performing a swinging motion with a parallel to the swing frame 4 arranged Schmidtschwingmasse 5, wherein the Gegenschwingmasse is supported elastically on a foundation 6.
  • a plurality of link elements 7 connects the swing frame 4 with the counterweight 5, while the link elements 7 are at an angle with respect to the vertical ⁇ and arranged parallel to each other.
  • spring elements 8 are arranged between the oscillating frame 4 and the counterweight 5, which form a right angle with the link elements 7.
  • Such vibrating machines are known to those skilled in the art, so that a more detailed explanation is omitted
  • the vibration drive 2 is designed as a slider crank drive. Further details of the eccentric drive / vibration drive 2 according to the invention can be found in the drawings, FIGS. 2 to 6 and in the following explanations.
  • This consists essentially of a mounted in a housing eccentric shaft 9, wherein the end-side bearing points 10 are supported on the counterweight 5.
  • the bearing points 10 are supported on the foundation 6.
  • the sliding-crank drive or vibration drive 2 transmits a vibratory conveying movement via a push rod 11 to the oscillating frame 4.
  • the transmitted vibratory conveying movement is represented by the double-headed arrow 12 in FIG. 4.
  • the push rod 11 is coupled to a surrounding the eccentric housing member 13 of a drive bearing 14.
  • FIGS. 3 and 4 From the sectional view of Fig. 3 it can be seen that in the region of the drive bearing 14, which is formed in the embodiment as a spherical roller bearing, between the drive bearing 14 and the eccentric shaft 9, an eccentrically shaped sleeve is arranged.
  • the eccentric shaft 9 is rotatably received about the longitudinal axis 16 in the eccentric sleeve 15, wherein the eccentric portion of the eccentric shaft 9 and the eccentric sleeve 15 are arranged radially superimposed.
  • the eccentricity of the eccentric shaft 9 is shown in FIGS. 3 and 4 by the dot-dash line e1, the eccentricity of the eccentric sleeve 15 is shown by the dotted line e2.
  • This fixing means 17 can be designed such that it causes a positive and / or non-positive fixation.
  • a hydromechanical fixing means 17 is shown.
  • This hydromechanical fixing means 17 consists of a double-walled sleeve element wherein between outer ring member 19 and inner ring member 20, a closed annular chamber 21 is formed.
  • the chamber 21 is divided by a ring-shaped piston 22 into two pressure medium chambers 23/24, which are filled with pressure medium and are in communication with a corresponding inflow / outflow line.
  • a special feature of the piston 22 is that the piston 22 is conically widening with respect to its outer circumferential surface.
  • the inner circumferential surface of the outer ring member 19 of the sleeve member 18 is formed adapted according to the cone of the piston 22.
  • the sleeve member 18 is disposed on an eccentric portion of the eccentric shaft 9 adjacent cylindrical shaft portion 25.
  • the sleeve member 18 is at the outer radial shell portion of the outer ring member 19 in a radially expanding cylinder housing portion 26, which adjoins the eccentrically shaped portion of the eccentric sleeve.
  • FIGS. 3 and 4 another embodiment of a fixing means 17 'is shown and explained in more detail below.
  • the same parts already described above are provided in the figures 5 and 6 with the same reference numerals and will not be explained at this point.
  • a mechanical fixing means 17 ' is arranged in the further exemplary embodiment.
  • This mechanical fixing means 17 ' causes a non-positive fixation and consists essentially of an eccentric sleeve 15' with slotted radially extending cylindrical housing portion 26 '.
  • the eccentric sleeve 15 ' is arranged between the drive bearing 14 and the eccentric shaft 9.
  • the eccentric shaft 9 is rotatably received about the longitudinal axis 16 in the eccentric sleeve 15 ', wherein the eccentric portion of the eccentric shaft and the eccentric sleeve 15' are arranged radially superimposed.
  • the position between eccentric shaft 9 and eccentric sleeve 15 ' is secured. This is effected by the mechanical fixing means 17 '.
  • the eccentric sleeve 15 ' is radially expanding in a further section as a cylinder housing section 26'.
  • the cylinder housing portion 26 ' is, as can be seen from Fig. 6, designed transversely slotted, with clamping screws are provided which provide a force-locking clamping between the eccentric sleeve and eccentric shaft in the area cause the cylinder housing section.
  • a sleeve 28 is inserted from bearing metal, thereby seizing is to be prevented at this point.
  • This sliding bush made of bearing metal is shrunk onto the cylindrical shaft section 25.
  • bronze is used as the bearing metal.
  • corresponding coatings on the cylindrical shaft section 25 or the inner circumferential surface of the cylinder housing section 26 'could also be provided at this point.
  • the eccentric radius can be set from 0 to a maximum value.
  • the setting of an eccentricity of 0-8 mm is possible.
  • marks or a scaling are provided on the outer lateral surface of the cylinder housing section.
  • eccentric sleeve 15,15 'to the eccentric shaft 9 are on the eccentric sleeve 15,15' in communication radially expanding cylinder housing section 26,26 'grooves for a standardized hook wrench and at one end portion of the eccentric shaft 9 a square attached ,

Abstract

An eccentric shaft (9) has a rotational axis adjustable with respect to an eccentric cam case (15). A fixing mechanism (17), which locks the eccentric shaft at the adjusted position, is operable hydro mechanically and includes a casing (18) enclosing adjustable conical pistons (22) stored in cylinder housings (26). The pistons lock the eccentric shaft by wedging action. Clamping screws fasten the cylinder housings to the eccentric cam case.

Description

Schwingförderer sind Stetigförderer, die zum Fördern oder Behandeln von Schüttgütern und Stückgütern eingesetzt werden. Ein Einsatzgebiet von Schwingmaschinen liegt dabei zum Beispiel in Gießereien, wobei Gussstücke über längere Transportwege befördert und gleichzeitig behandelt werden können. Ein weiteres Einsatzgebiet ist zum Beispiel der Ascheaustrag bei Müllverbrennungsanlagen. Hierzu besitzen die Schwingmaschinen einen Förderboden, der in Rohr- oder Rinnenform ausgebildet werden kann. Ein sogenannter Schwingungsantrieb versetzt den Förderboden in eine periodische Schwingbewegung, wodurch eine Förderbewegung des auf dem Förderboden befindlichen Gutes erzielbar ist. Je nach Art und Größe des zu fördernden bzw. zu behandelnden Gutes werden in der Praxis unterschiedliche Schwingungsantriebe eingesetzt.Vibratory conveyors are continuous conveyors used to convey or treat bulk and general cargo. One application of vibrating machines is, for example, in foundries, whereby castings can be transported over longer transport routes and treated at the same time. Another area of use is, for example, the ash discharge in waste incineration plants. For this purpose, the vibrating machines have a conveyor bottom, which can be formed in tube or channel shape. A so-called vibration drive puts the conveyor floor in a periodic oscillating motion, whereby a conveying movement of the goods located on the conveyor floor can be achieved. Depending on the type and size of the material to be conveyed or treated, different vibration drives are used in practice.

Ein derartiger Schwingungsantrieb ist der sogenannte Schubkurbel- bzw. Exzenterantrieb. Dieser besteht im wesentlichen aus einer in einem Gehäuse drehbar gelagerten Exzenterwelle, wobei das Gehäuse über eine Schubstange mit dem Förderboden in Verbindung steht. Beim Einmassenschwinger ist dabei die Lagerung auf dem Fundament abgestützt, wobei beim Zweimassenschwinger die Lagerstellen auf der Gegenmasse abgestützt sind.Such a vibration drive is the so-called push crank or eccentric drive. This consists essentially of a rotatably mounted in a housing eccentric shaft, wherein the housing is connected via a push rod with the conveyor bottom. When single-mass oscillator while the bearing is supported on the foundation, wherein the dual mass oscillator bearing points are supported on the counterweight.

Die Schwingbewegung des Förderbodens wird im wesentlichen von der Schwingungszahl, der Schwingweite und dem Schwingwurfwinkel bestimmt, wobei von praktischem Interesse die Fördergeschwindigkeit und damit die Förderleistung ist. Die Fördergeschwindigkeit des zu fördernden Gutes ist beim Einsatz eines Schubkurbelantriebes unter anderem abhängig von dem fest vorgegebenen Exzenterradius der eingesetzten Exzenterwelle. Hierbei kann beim fest vorgegebenen Exzenterradius ein Antrieb nur für bestimmte zu fördernde Güter und Fördergeschwindigkeiten eingesetzt werden. Bei veränderten Einsatzbedingungen, muss hierbei der gesamte Schubkurbelantrieb ausgetauscht und/oder umgebaut werden. Dies erfordert aufwendige Montage bzw. Umrüstarbeiten, die mit hohen Kosten und langen Montagezeiten bzw. Stillstandszeiten des Schwingförderers und der damit in Verbindung stehenden Anlagenteile verbunden sind.The oscillatory movement of the conveyor floor is essentially determined by the number of oscillations, the amplitude and the swing angle, with practical interest, the conveying speed and thus the flow rate. The conveying speed of the material to be conveyed is Use of a sliding-crank drive, among other things depending on the fixed eccentric radius of the eccentric shaft used. In this case, a drive can be used only for certain goods to be conveyed and delivery speeds at the fixed eccentric radius. If the operating conditions change, the entire thrust crank drive must be replaced and / or rebuilt. This requires complex assembly or retooling, which are associated with high costs and long assembly times and downtime of the vibratory conveyor and the associated system parts.

Aufgabe der vorliegenden Erfindung ist es daher einen Exzenterantrieb für Schwingmaschinen derart weiterzubilden, dass bei veränderten Einsatzbedingungen eine schnelle und einfache Veränderung der Schwingdaten insbesondere der Fördergeschwindigkeit des Schwingungsförderers möglich ist.The object of the present invention is therefore to develop an eccentric drive for vibrating machines in such a way that, under changed conditions of use, a quick and simple change of the vibration data, in particular the conveying speed of the vibration conveyor, is possible.

Diese Aufgabe wird dadurch gelöst, dass der erfindungsgemäße Schwingungsantrieb eine exzentrische Welle (Exzenterwelle) umfasst, die in einer exzentrischen Hülse (Exzenterhülse) gelagert ist und die Position zwischen Exzenterwelle und Exzenterhülse beliebig zueinander eingestellt werden kann. Hierdurch kann der Exzenterradius in einem sehr weiten Bereich in Millimeter-Schritten verändert werden. Bei veränderten Einsatzbedingungen kann somit ohne aufwendige Umrüstarbeiten eine erforderliche Exzentrizität eingestellt werden.This object is achieved in that the vibration drive according to the invention comprises an eccentric shaft (eccentric shaft) which is mounted in an eccentric sleeve (eccentric sleeve) and the position between the eccentric shaft and the eccentric sleeve can be set arbitrarily. As a result, the eccentric radius can be changed in a very wide range in millimeter increments. With changed operating conditions, a required eccentricity can thus be set without expensive retooling.

Die eingestellte Position wird dann über kraft- und/oder formschlüssige Mittel fixiert.The set position is then fixed by non-positive and / or positive locking means.

In einer bevorzugten Ausführungsform der Erfindung sind hydromechanische Fixiermittel vorgesehen, wobei ein hydraulisches Hülsenelement zum Klemmen und Lösen der Position der Exzenterwelle und der Exzenterhülse angeordnet ist. Durch entsprechende Druckbeaufschlagung eines in einem Zylindergehäuseabschnittes verschiebbar angeordneten konisch ausgebildeten Kolbens kann dabei sehr schnell ein Klemmen bzw. Lösen der Position der Exzenterwelle zur Exzenterhülse vorgenommen werden. Zwecks einfacher Einstellung und Justierung eines Exzenterradius sind am Außenumfang des das Hülsenelement umgebenden Zylindergehäuseabschnittes Markierungen vorgesehen.In a preferred embodiment of the invention hydromechanical fixing means are provided, wherein a hydraulic sleeve member for clamping and releasing the position of the eccentric shaft and the eccentric sleeve is arranged. By appropriate pressurization of a displaceably arranged in a cylinder housing portion conical piston can be made very quickly a terminals or releasing the position of the eccentric shaft to the eccentric sleeve. For ease of adjustment and adjustment of an eccentric radius marks are provided on the outer circumference of the cylinder housing portion surrounding the sleeve member.

In einer weiteren Ausbildung des Erfindungsgedankens ist das Fixiermittel derart ausgebildet, dass ein kraftschlüssiges Fixieren der Position der Exzenterwelle zu der Exzenterhülse mittels mechanischer Klemmung bewirkt wird. Hierfür ist die Exzenterhülse geschlitzt ausgeführt, wobei die Klemmung über eine Schraube einstellbar ist. Vorteilhaft bei dieser mechanischen Klemmung ist, dass der Aufbau des Fixiermittels einfach und daher in den Herstellungskosten niedrig ist. Desweiteren wird zum Lösen und Klemmen kein teures Spezialwerkzeug sowie Druckmittel in Form von synthetischen oder mineralischen Ölen benötigt.In a further embodiment of the inventive concept, the fixing means is designed such that a non-positive fixing of the position of the eccentric shaft to the eccentric sleeve is effected by means of mechanical clamping. For this purpose, the eccentric sleeve is designed slotted, the clamp is adjustable by a screw. An advantage of this mechanical clamping is that the structure of the fixing agent is simple and therefore low in manufacturing costs. Furthermore, no expensive special tool and pressure medium in the form of synthetic or mineral oils is needed for loosening and clamping.

Aufgrund des generatorischen Betriebes des Schubkurbelantriebes (Rückstöße treten auf) sind formschlüssige Verbindungen durch die auftretenden Scherkräfte minder geeignet. Bei den formschlüssigen Verbindungen können aufgrund der auftretenden Belastungen Keilverzahnungen eingesetzt werden, wobei eine Keilverzahnung hinsichtlich der Herstellungskosten sehr teuer ist.Due to the regenerative operation of the sliding crank drive (recoils occur) positive connections are less suitable by the shear forces occurring. In the positive connections, splines can be used due to the loads occurring, with a spline is very expensive in terms of manufacturing costs.

Beim Einsatz eines Fixiermittels, welches ein kraftschlüssiges Klemmen bewirkt, ist ein dauerhafter störungsfreier Betrieb der Schwingmaschine möglich.When using a fixing agent, which causes a force-locking terminals, a permanent trouble-free operation of the vibrating machine is possible.

Die Erfindung wird anhand eines Ausführungsbeispiels, das in den Zeichnungen dargestellt ist, näher beschrieben.The invention will be described in more detail with reference to an embodiment shown in the drawings.

Es zeigt:

Fig. 1:
eine schematische Darstellung einer Schwingmaschine,
Fig. 2:
eine vergrößerte Darstellung der Einbausituation des Schwingungsantriebs in Seitenansicht,
Fig. 3:
eine Schnittdarstellung der Exzenterwelle mit Exzenterhülse samt Lagerstellen,
Fig. 4:
einen Querschnitt durch die Exzenterwelle mit Exzenterhülse längs der Linie IV-IV in Fig. 3,
Fig. 5:
eine weitere Ausführungsform der Exzenterwelle mit Exzenterhülse in Schnittdarstellung,
Fig. 6:
einen Querschnitt durch die Exzenterwelle mit Exzenterhülse längs der Linie B - B in Fig. 5.
It shows:
Fig. 1:
a schematic representation of a vibrating machine,
Fig. 2:
an enlarged view of the installation situation of the vibration drive in side view,
3:
a sectional view of the eccentric shaft with eccentric sleeve, including bearings,
4:
a cross section through the eccentric shaft with eccentric sleeve along the line IV-IV in Fig. 3,
Fig. 5:
a further embodiment of the eccentric shaft with eccentric sleeve in a sectional view,
Fig. 6:
a cross section through the eccentric shaft with eccentric sleeve along the line B - B in Fig. 5th

In Fig. 1 ist in schematischer Darstellung eine Schwingmaschine 1 mit dem erfindungsgemäßen Schwingungsantrieb 2 dargestellt. Die Schwingmaschine 1 ist als Schwingförderer zum Fördern von Stückgut zum Beispiel Gussstücke ausgebildet. Es sind jedoch auch beliebig andere Einsatzgebiete möglich. Der Schwingförderer 1 kann dabei auch als Schwingsieb ausgebildet sein. Der Schwingförderer 1 besitzt einen Förderboden 3, der in einem Schwingrahmen 4 angeordnet ist. Der Schwingrahmen 4 ist zwecks Ausführung einer Schwingbewegung mit einer parallel zum Schwingrahmen 4 angeordneten Gegenschwingmasse 5 gekoppelt, wobei die Gegenschwingmasse elastisch auf einem Fundament 6 abgestützt ist. Eine Vielzahl von Lenkerelementen 7 verbindet den Schwingrahmen 4 mit der Gegenschwingmasse 5, dabei sind die Lenkerelemente 7 in Bezug auf die Vertikale unter einem Winkel α und parallel zueinander angeordnet. Des weiteren sind Federelemente 8 zwischen dem Schwingrahmen 4 und der Gegenschwingmasse 5 angeordnet, die einen rechten Winkel mit den Lenkerelementen 7 bilden. Derartige Schwingmaschinen sind dem Fachmann bekannt, so dass auf eine nähere Erläuterung an dieser Stelle verzichtet wird.In Fig. 1, a vibrating machine 1 is shown with the vibration drive 2 according to the invention in a schematic representation. The vibrating machine 1 is designed as a vibrating conveyor for conveying piece goods, for example, castings. However, any other fields of use are possible. The vibratory conveyor 1 can also be designed as a vibrating screen. The vibratory conveyor 1 has a conveyor bottom 3, which is arranged in a swing frame 4. The swing frame 4 is coupled for the purpose of performing a swinging motion with a parallel to the swing frame 4 arranged Gegenschwingmasse 5, wherein the Gegenschwingmasse is supported elastically on a foundation 6. A plurality of link elements 7 connects the swing frame 4 with the counterweight 5, while the link elements 7 are at an angle with respect to the vertical α and arranged parallel to each other. Furthermore, spring elements 8 are arranged between the oscillating frame 4 and the counterweight 5, which form a right angle with the link elements 7. Such vibrating machines are known to those skilled in the art, so that a more detailed explanation is omitted here.

Der erfindungsgemäße Schwingungsantrieb 2 ist als Schubkurbelantrieb ausgebildet. Nähere Einzelheiten zu dem erfindungsgemäßen Exzenterantrieb / Schwingungsantrieb 2 sind den Zeichnungen Fig. 2 bis Fig. 6 sowie den nachfolgenden Erläuterungen zu entnehmen. Dieser besteht im wesentlichen aus einer in einem Gehäuse gelagerten Exzenterwelle 9, wobei die endseitig angeordneten Lagerstellen 10 auf der Gegenschwingmasse 5 abgestützt sind. Bei einer Ausführung als Einmassenschwinger sind die Lagerstellen 10 auf dem Fundament 6 abgestützt. Der Schubkurbelantrieb bzw. Schwingungsantrieb 2 überträgt eine Schwingförderbewegung über eine Schubstange 11 auf den Schwingrahmen 4. Die übertragene Schwingförderbewegung ist durch den Doppelpfeil 12 in Fig. 4 dargestellt. Dazu ist die Schubstange 11 an ein die Exzenterwelle umgebendes Gehäuseelement 13 eines Antriebslagers 14 gekoppelt.The vibration drive 2 according to the invention is designed as a slider crank drive. Further details of the eccentric drive / vibration drive 2 according to the invention can be found in the drawings, FIGS. 2 to 6 and in the following explanations. This consists essentially of a mounted in a housing eccentric shaft 9, wherein the end-side bearing points 10 are supported on the counterweight 5. In one embodiment as a single-mass oscillator, the bearing points 10 are supported on the foundation 6. The sliding-crank drive or vibration drive 2 transmits a vibratory conveying movement via a push rod 11 to the oscillating frame 4. The transmitted vibratory conveying movement is represented by the double-headed arrow 12 in FIG. 4. For this purpose, the push rod 11 is coupled to a surrounding the eccentric housing member 13 of a drive bearing 14.

Aus der Schnittdarstellung der Fig. 3 ist zu ersehen, dass im Bereich des Antriebslagers 14, welches in dem Ausführungsbeispiel als Pendelrollenlager ausgebildet ist, zwischen Antriebslager 14 und Exzenterwelle 9 eine exzentrisch ausgebildete Hülse angeordnet ist. Die Exzenterwelle 9 ist dabei verdrehbar um die Längsachse 16 in der Exzenterhülse 15 aufgenommen, wobei der exzentrische Abschnitt der Exzenterwelle 9 und der Exzenterhülse 15 radial übereinanderliegend angeordnet sind. Die Exzentrizität der Exzenterwelle 9 ist in den Fig. 3 und Fig. 4 durch die strichpunktierte Linie e1, die Exzentrizität der Exzenterhülse 15 ist durch die strichpunktierte Linie e2 dargestellt.From the sectional view of Fig. 3 it can be seen that in the region of the drive bearing 14, which is formed in the embodiment as a spherical roller bearing, between the drive bearing 14 and the eccentric shaft 9, an eccentrically shaped sleeve is arranged. The eccentric shaft 9 is rotatably received about the longitudinal axis 16 in the eccentric sleeve 15, wherein the eccentric portion of the eccentric shaft 9 and the eccentric sleeve 15 are arranged radially superimposed. The eccentricity of the eccentric shaft 9 is shown in FIGS. 3 and 4 by the dot-dash line e1, the eccentricity of the eccentric sleeve 15 is shown by the dotted line e2.

Die Position zwischen Exzenterwelle 9 und Exzenterhülse 15 ist gesichert. Es ist deshalb notwendig ein entsprechendes Fixiermittel 17 vorzusehen. Dieses Fixiermittel 17 kann dabei derart ausgebildet sein, dass es eine formschlüssige und/oder kraftschlüssige Fixierung bewirkt. In dem in den Figuren 3 und 4 dargestellten Ausführungsbeispiel ist ein hydromechanisches Fixiermittel 17 gezeigt. Dieses hydromechanische Fixiermittel 17 besteht aus einem doppelwandig ausgebildeten Hülsenelement wobei zwischen äußerem Ringelement 19 und innerem Ringelement 20 eine geschlossene ringförmige Kammer 21 gebildet wird. Die Kammer 21 wird durch einen ringförmig ausgebildeten Kolben 22 in zwei Druckmittelkammern 23/24 unterteilt, die mit Druckmittel gefüllt sind und mit einer entsprechenden Zu- / Abflussleitung in Verbindung stehen. Eine Besonderheit des Kolbens 22 besteht darin, dass der Kolben 22 in Bezug auf seine äußere Mantelfläche konisch sich erweiternd ausgebildet ist. Die innere Mantelfläche des äußeren Ringelementes 19 des Hülsenelementes 18 ist entsprechend dem Konus des Kolbens 22 angepasst ausgebildet. Das Hülsenelement 18 ist auf einem dem Exzenterabschnitt der Exzenterwelle 9 benachbarten zylindrischen Wellenabschnitt 25 angeordnet. Das Hülsenelement 18 ist dabei an dem äußeren radialen Mantelabschnitt des äußeren Ringelementes 19 in einem radial sich erweiternden Zylindergehäuseabschnitt 26, der sich an dem exzentrisch ausgebildeten Abschnitt der Exzenterhülse anschließt. An einem Endbereich des Hülsenelementes 18, der aus dem Zylindergehäuseabschnitt 26 herausragt sind Hydraulikanschlüsse 27 angeordnet, die eine entsprechende Druckbeaufschlagung der Druckmittelkammern 23/24 rechts/links und somit eine Verschiebung des Kolbens 22 nach rechts bzw. links bewirken. Durch eine Druckbeaufschlagung der rechten Druckmittelkammer 23 wird somit ein Verschieben des Kolbens 22 nach links erzielt, wodurch ein kraftschlüssiges Verspannen der Exzenterhülse 15 mit der Exzenterwelle 9 erreicht wird.The position between the eccentric shaft 9 and eccentric sleeve 15 is secured. It is therefore necessary to provide a corresponding fixing 17. This fixing means 17 can be designed such that it causes a positive and / or non-positive fixation. In the exemplary embodiment illustrated in FIGS. 3 and 4, a hydromechanical fixing means 17 is shown. This hydromechanical fixing means 17 consists of a double-walled sleeve element wherein between outer ring member 19 and inner ring member 20, a closed annular chamber 21 is formed. The chamber 21 is divided by a ring-shaped piston 22 into two pressure medium chambers 23/24, which are filled with pressure medium and are in communication with a corresponding inflow / outflow line. A special feature of the piston 22 is that the piston 22 is conically widening with respect to its outer circumferential surface. The inner circumferential surface of the outer ring member 19 of the sleeve member 18 is formed adapted according to the cone of the piston 22. The sleeve member 18 is disposed on an eccentric portion of the eccentric shaft 9 adjacent cylindrical shaft portion 25. The sleeve member 18 is at the outer radial shell portion of the outer ring member 19 in a radially expanding cylinder housing portion 26, which adjoins the eccentrically shaped portion of the eccentric sleeve. At an end portion of the sleeve member 18, which protrudes from the cylinder housing portion 26 hydraulic connections 27 are arranged, which cause a corresponding pressurization of the pressure fluid chambers 23/24 right / left and thus a displacement of the piston 22 to the right or left. By pressurizing the right-hand pressure medium chamber 23, a displacement of the piston 22 is thus achieved to the left, whereby a force-locking clamping of the eccentric sleeve 15 is achieved with the eccentric shaft 9.

Diese kraftschlüssige Kopplung wird durch Druckbeaufschlagung der linken Druckmittelkammer 24 aufgehoben, da dadurch der Kolben 22 nach rechts geschoben wird und die Verspannung gelöst wird.This frictional coupling is canceled by pressurization of the left pressure medium chamber 24, since thereby the piston 22 is pushed to the right and the tension is released.

In den Figuren 5 und 6 ist ein weiteres Ausführungsbeispiel eines Fixiermittels 17' dargestellt und nachfolgend näher erläutert. Gleiche bereits zuvor beschriebene Teile sind in den Figuren 5 und 6 mit denselben Bezugszeichen versehen und werden an dieser Stelle nicht erläutert. Im Unterschied zu dem in den Figuren 3 und 4 dargestellten hydromechanischen Fixiermittel 17 ist in dem weiteren Ausführungsbeispiel ein mechanisches Fixiermittel 17' angeordnet. Dieses mechanische Fixiermittel 17' bewirkt eine kraftschlüssige Fixierung und besteht im wesentlichen aus einer Exzenterhülse 15' mit geschlitzt ausgeführtem radial sich erweiternden Zylindergehäuseabschnitt 26'.In the figures 5 and 6, another embodiment of a fixing means 17 'is shown and explained in more detail below. The same parts already described above are provided in the figures 5 and 6 with the same reference numerals and will not be explained at this point. In contrast to the hydromechanical fixing means 17 shown in FIGS. 3 and 4, a mechanical fixing means 17 'is arranged in the further exemplary embodiment. This mechanical fixing means 17 'causes a non-positive fixation and consists essentially of an eccentric sleeve 15' with slotted radially extending cylindrical housing portion 26 '.

Wie zu den Figuren 3 und 4 beschrieben, ist die Exzenterhülse 15' zwischen Antriebslager 14 und Exzenterwelle 9 angeordnet. Die Exzenterwelle 9 ist dabei verdrehbar um die Längsachse 16 in der Exzenterhülse 15' aufgenommen, wobei der exzentrische Abschnitt der Exzenterwelle und der Exzenterhülse 15' radial übereinander liegend angeordnet sind. Die Position zwischen Exzenterwelle 9 und Exzenterhülse 15' ist gesichert. Dies wird durch das mechanische Fixiermittel 17' bewirkt. Um die Fixierung der Position zwischen Exzenterwelle und Exzenterhülse zu erzielen, ist dabei die Exzenterhülse 15' in einem weiteren Abschnitt radial sich erweiternd als Zylindergehäuseabschnitt 26' ausgebildet. Dieser schließt sich an dem exzentrisch ausgebildeten Abschnitt der Exzenterhülse an. Der Zylindergehäuseabschnitt 26' ist, wie es aus der Fig. 6 zu ersehen ist, quer geschlitzt ausgeführt, wobei Klemmschrauben vorgesehen sind, die ein kraftschlüssiges Klemmen zwischen Exzenterhülse und Exzenterwelle im Bereich des Zylindergehäuseabschnittes bewirken. Zwischen Zylindergehäuseabschnitt 26' und dem zylindrischen Wellenabschnitt 25 ist eine Hülse 28 aus Lagermetall eingefügt, wodurch ein Fressen an dieser Stelle verhindert werden soll. Diese Gleitbuchse aus Lagermetall ist auf den zylindrischen Wellenabschnitt 25 aufgeschrumpft. Als Lagermetall wird beispielsweise Bronze verwendet. Anstelle des Einsatzes einer Hülse 28 aus Lagermetall könnten an dieser Stelle auch entsprechende Beschichtungen auf dem zylindrischen Wellenabschnitt 25 bzw. der inneren Mantelfläche des Zylindergehäuseabschnittes 26' vorgesehen werden.As described with reference to FIGS. 3 and 4, the eccentric sleeve 15 'is arranged between the drive bearing 14 and the eccentric shaft 9. The eccentric shaft 9 is rotatably received about the longitudinal axis 16 in the eccentric sleeve 15 ', wherein the eccentric portion of the eccentric shaft and the eccentric sleeve 15' are arranged radially superimposed. The position between eccentric shaft 9 and eccentric sleeve 15 'is secured. This is effected by the mechanical fixing means 17 '. In order to achieve the fixation of the position between the eccentric shaft and the eccentric sleeve, the eccentric sleeve 15 'is radially expanding in a further section as a cylinder housing section 26'. This adjoins the eccentrically formed portion of the eccentric sleeve. The cylinder housing portion 26 'is, as can be seen from Fig. 6, designed transversely slotted, with clamping screws are provided which provide a force-locking clamping between the eccentric sleeve and eccentric shaft in the area cause the cylinder housing section. Between cylinder housing portion 26 'and the cylindrical shaft portion 25, a sleeve 28 is inserted from bearing metal, thereby seizing is to be prevented at this point. This sliding bush made of bearing metal is shrunk onto the cylindrical shaft section 25. For example, bronze is used as the bearing metal. Instead of using a sleeve 28 made of bearing metal, corresponding coatings on the cylindrical shaft section 25 or the inner circumferential surface of the cylinder housing section 26 'could also be provided at this point.

Wenn die kraftschlüssige Kopplung aufgehoben ist, kann die Position zwischen Exzenterwelle 9 und Exzenterhülse 15,15' durch einfaches Verdrehen der beiden Bauteile zueinander verändert werden.If the frictional coupling is canceled, the position between the eccentric shaft 9 and eccentric sleeve 15,15 'can be changed by simply rotating the two components to each other.

Hierdurch kann der Exzenterradius von O bis zu einem Maximalwert eingestellt werden. In dem dargestellten Ausführungsbeispiel ist die Einstellung einer Exzentrizität von 0 - 8 mm möglich.As a result, the eccentric radius can be set from 0 to a maximum value. In the illustrated embodiment, the setting of an eccentricity of 0-8 mm is possible.

Um eine einfache Einstellbarkeit für den Bediener zu erhalten, sind an der äußeren Mantelfläche des Zylindergehäuseabschnittes Markierungen bzw. eine Skalierung vorgesehen.In order to obtain an easy adjustability for the operator, marks or a scaling are provided on the outer lateral surface of the cylinder housing section.

Zur einfachen und bedienerfreundlichen Verdrehung der Exzenterhülse 15,15' zur Exzenterwelle 9 sind an dem mit der Exzenterhülse 15,15' in Verbindung stehenden radial sich erweiternden Zylindergehäuseabschnitt 26,26' Nuten für einen normierten Hakenschlüssel und an einem Endbereich der Exzenterwelle 9 ein Vierkant angebracht.For easy and user-friendly rotation of the eccentric sleeve 15,15 'to the eccentric shaft 9 are on the eccentric sleeve 15,15' in communication radially expanding cylinder housing section 26,26 'grooves for a standardized hook wrench and at one end portion of the eccentric shaft 9 a square attached ,

Claims (6)

Schwingungsantrieb, insbesondere Exzenterantrieb für Schwingmaschinen, umfassend eine drehbar antreibbare Exzenterwelle (9), die mindestens einen exzentrischen Abschnitt aufweist sowie eine den exzentrischen Abschnitt umgebende Exzenterhülse (15,15'), die am Außenumfang mindestens einen exzentrischen Abschnitt aufweist und wobei die Exzentrizität des Schwingungsantriebes (2) durch Verdrehen der Position der Exzenterwelle (9) zu der Exzenterhülse (15,15') einstellbar ist und die eingestellte Position durch Fixiermittel (17,17') arretierbar ist.Vibration drive, in particular eccentric drive for vibrating machines, comprising a rotatably driven eccentric shaft (9) having at least one eccentric portion and an eccentric portion surrounding the eccentric sleeve (15,15 ') having at least one eccentric portion on the outer circumference and wherein the eccentricity of the vibration drive (2) by rotation of the position of the eccentric shaft (9) to the eccentric sleeve (15,15 ') is adjustable and the set position by fixing means (17,17') can be locked. Schwingungsantrieb, insbesondere Exzenterantrieb für Schwingmaschinen nach Patentanspruch 1, wobei die Fixiermittel (17,17') ein formschlüssiges und/oder kraftschlüssiges Fixieren der Position der Exzenterwelle (9) zu der Exzenterhülse (15,15') bewirken.Vibration drive, in particular eccentric drive for vibrating machines according to claim 1, wherein the fixing means (17,17 ') cause a positive and / or non-positive fixing of the position of the eccentric shaft (9) to the eccentric sleeve (15,15'). Schwingungsantrieb, insbesondere Exzenterantrieb für Schwingmaschinen nach Patentanspruch 1 oder 2, wobei die Fixiermittel (17) ein hydromechanisch betätigbares Hülsenelement (18) umfassen, das zwischen Exzenterwelle (9) und Exzenterhülse (15) angeordnet ist und mittels entsprechender Druckbeaufschlagung ein in einer Kammer des Hülsenelementes (18) gelagerter konisch ausgebildeter ringförmiger Kolben (22) verschiebbar ist.Vibration drive, in particular eccentric drive for vibrating machines according to claim 1 or 2, wherein the fixing means (17) comprise a hydromechanically operable sleeve member (18) disposed between the eccentric shaft (9) and eccentric sleeve (15) and by means of appropriate pressurization in a chamber of the sleeve member (18) mounted conical annular piston (22) is displaceable. Schwingungsantrieb, insbesondere Exzenterantrieb für Schwingmaschinen nach einem der vorgenannten Patentansprüche, wobei das Hülsenelement (18) in einem Zylindergehäuseabschnitt (26) gelagert ist und der Zylindergehäuseabschnitt (26) an seiner äußeren Mantelfläche mit Markierungen versehen ist.Vibration drive, in particular eccentric drive for vibrating machines according to one of the preceding claims, wherein the sleeve member (18) in a cylinder housing portion (26) is mounted and the cylinder housing portion (26) is provided on its outer lateral surface with markings. Schwingungsantrieb, insbesondere Exzenterantrieb für Schwingmaschinen nach Patentanspruch 1 oder 2, wobei die Fixiermittel (17') einen quer geschlitzt ausgeführten Zylindergehäuseabschnitt (26') umfassen und wobei der Zylindergehäuseabschnitt (26') mit der Exzenterhülse (15') in Verbindung steht und mittels Klemmschrauben eine Veränderung der Schlitzweite am Zylindergehäuseabschnitt (26') erzielbar und somit eine mechanische Klemmung der Exzenterhülse (15') auf der Exzenterwelle (9) bewirkt wird.Vibration drive, in particular eccentric drive for vibrating machines according to claim 1 or 2, wherein the fixing means (17 ') comprise a cylinder housing section (26') designed transversely slotted and wherein the cylinder housing section (26 ') is in communication with the eccentric sleeve (15') and by means of clamping screws a change in the slot width on the cylinder housing portion (26 ') can be achieved and thus a mechanical clamping of the eccentric sleeve (15') on the eccentric shaft (9) is effected. Schwingungsantrieb, insbesondere Exzenterantrieb für Schwingmaschinen nach Patentanspruch 5, wobei Exzenterhülse (15') und Zylindergehäuseabschnitt (26') einteilig ausgebildet sind.Vibration drive, in particular eccentric drive for vibrating machines according to claim 5, wherein eccentric sleeve (15 ') and cylinder housing portion (26') are integrally formed.
EP20060004701 2005-03-26 2006-03-08 Oscillating drive especially eccentric drive for vibrating machines Not-in-force EP1704929B1 (en)

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DE200510014014 DE102005014014B4 (en) 2005-03-26 2005-03-26 Vibration drive, in particular eccentric drive for vibrating machines

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EP1704929B1 EP1704929B1 (en) 2009-07-15

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US3771374A (en) * 1971-08-16 1973-11-13 Russel Finex Out-of-balance weight assemblies
US3909147A (en) * 1974-11-07 1975-09-30 Raygo Inc Variable amplitude vibration generator
US4105356A (en) * 1977-05-19 1978-08-08 Koehring Corporation Vibratory roller
US4121472A (en) * 1975-11-29 1978-10-24 Koehring Gmbh - Bomag Division Eccentric drive
US4481835A (en) * 1981-10-28 1984-11-13 Dynapac Maskin Ab Device for continuous adjustment of the vibration amplitude of eccentric elements
US4561319A (en) * 1983-01-26 1985-12-31 Dynapac Ab Arrangement for journalling large eccentric forces
CH658413A5 (en) * 1983-06-08 1986-11-14 Ernst A Huber Vibratory shaft for machines with an oscillating mode of operation
DE3610123A1 (en) * 1986-03-26 1987-10-01 Bosch Gmbh Robert Method and apparatus for conveying material of small volume
DE4022089A1 (en) * 1989-07-15 1991-01-24 Prinzing Georg Gmbh Co Kg Casting concrete pipes by vibration process - uses cylindrical mould with vibrators mounted inside mould core
WO2000005455A1 (en) * 1998-07-13 2000-02-03 Rune Sturesson Rotatable eccentric device

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB769547A (en) * 1955-05-13 1957-03-06 Gerhard Lehmann Pottkamper Improvements in or relating to mechanical vibrators

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3771374A (en) * 1971-08-16 1973-11-13 Russel Finex Out-of-balance weight assemblies
US3909147A (en) * 1974-11-07 1975-09-30 Raygo Inc Variable amplitude vibration generator
US4121472A (en) * 1975-11-29 1978-10-24 Koehring Gmbh - Bomag Division Eccentric drive
US4105356A (en) * 1977-05-19 1978-08-08 Koehring Corporation Vibratory roller
US4481835A (en) * 1981-10-28 1984-11-13 Dynapac Maskin Ab Device for continuous adjustment of the vibration amplitude of eccentric elements
US4561319A (en) * 1983-01-26 1985-12-31 Dynapac Ab Arrangement for journalling large eccentric forces
CH658413A5 (en) * 1983-06-08 1986-11-14 Ernst A Huber Vibratory shaft for machines with an oscillating mode of operation
DE3610123A1 (en) * 1986-03-26 1987-10-01 Bosch Gmbh Robert Method and apparatus for conveying material of small volume
DE4022089A1 (en) * 1989-07-15 1991-01-24 Prinzing Georg Gmbh Co Kg Casting concrete pipes by vibration process - uses cylindrical mould with vibrators mounted inside mould core
WO2000005455A1 (en) * 1998-07-13 2000-02-03 Rune Sturesson Rotatable eccentric device

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EP1704929B1 (en) 2009-07-15
DE102005014014B4 (en) 2008-04-03
DE502006004215D1 (en) 2009-08-27
ES2326677T3 (en) 2009-10-16
DE102005014014A1 (en) 2006-10-05

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